JP2016200947A - Pressure regulating valve - Google Patents
Pressure regulating valve Download PDFInfo
- Publication number
- JP2016200947A JP2016200947A JP2015080130A JP2015080130A JP2016200947A JP 2016200947 A JP2016200947 A JP 2016200947A JP 2015080130 A JP2015080130 A JP 2015080130A JP 2015080130 A JP2015080130 A JP 2015080130A JP 2016200947 A JP2016200947 A JP 2016200947A
- Authority
- JP
- Japan
- Prior art keywords
- spring receiving
- vibration absorbing
- spring
- absorbing member
- housing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Ceased
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/20—Excess-flow valves
- F16K17/22—Excess-flow valves actuated by the difference of pressure between two places in the flow line
- F16K17/24—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member
- F16K17/28—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in one direction only
- F16K17/30—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in one direction only spring-loaded
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D16/00—Control of fluid pressure
- G05D16/04—Control of fluid pressure without auxiliary power
- G05D16/10—Control of fluid pressure without auxiliary power the sensing element being a piston or plunger
- G05D16/107—Control of fluid pressure without auxiliary power the sensing element being a piston or plunger with a spring-loaded piston in combination with a spring-loaded slideable obturator that move together over range of motion during normal operation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K47/00—Means in valves for absorbing fluid energy
- F16K47/02—Means in valves for absorbing fluid energy for preventing water-hammer or noise
Abstract
Description
本発明は、流体の供給経路に設けられている圧力調整弁に関する。 The present invention relates to a pressure regulating valve provided in a fluid supply path.
流体の一例である気体燃料を使用する内燃機関の燃料供給系には、燃料タンクから供給された気体燃料の圧力を減圧する圧力調整弁と、同圧力調整弁によって減圧された気体燃料が供給されるデリバリパイプと、デリバリパイプ内の気体燃料を噴射して吸気通路内に供給する噴射弁とが設けられている。 A fuel supply system of an internal combustion engine that uses gaseous fuel, which is an example of a fluid, is supplied with a pressure regulating valve that depressurizes the pressure of the gaseous fuel supplied from the fuel tank, and gaseous fuel decompressed by the pressure regulating valve. A delivery pipe and an injection valve that injects gaseous fuel in the delivery pipe and supplies the fuel into the intake passage.
特許文献１には、こうした燃料噴射系に使用することのできる圧力調整弁の一例が記載されている。すなわち、図８に示すように、圧力調整弁は有底筒状をなすハウジング１１０を備えており、同ハウジング１１０は、図中上下方向である軸方向における一端及び他端に開口する筒体１１１と、筒体１１１の図中上部開口を閉塞する蓋体１１２とを有している。そして、このハウジング１１０内には、軸方向に進退移動するピストン１２０と、蓋体１１２から離れる方向である図中下方への付勢力をピストン１２０に付与するスプリング１３０と、スプリング１３０の図中上端を支持するばね受け部材１４０とが設けられている。また、蓋体１１２は調整スクリュ１５０を支持しており、調整スクリュ１５０はその図中下端である先端でばね受け部材１４０を支持している。 Patent Document 1 describes an example of a pressure regulating valve that can be used in such a fuel injection system. That is, as shown in FIG. 8, the pressure regulating valve includes a housing 110 having a bottomed cylindrical shape, and the housing 110 opens at one end and the other end in the axial direction which is the vertical direction in the figure. And a lid body 112 that closes the upper opening of the cylindrical body 111 in the figure. In the housing 110, a piston 120 that moves forward and backward in the axial direction, a spring 130 that applies a downward urging force in the figure, which is away from the lid 112, to the piston 120, and an upper end of the spring 130 in the figure. And a spring receiving member 140 for supporting the. Moreover, the cover body 112 supports the adjustment screw 150, and the adjustment screw 150 supports the spring receiving member 140 at the tip which is the lower end in the figure.
こうした圧力調整弁にあっては、デリバリパイプ内の燃料圧力が低くなると、同デリバリパイプ内と連通する調圧室１６０内の圧力が低くなり、ピストン１２０が図中下方に移動する。すると、圧力調整弁の開度が大きくなり、デリバリパイプ内への気体燃料の流出量が多くなる。一方、デリバリパイプ内の燃料圧力が高くなると、調圧室１６０内の圧力が高くなり、スプリング１３０からの付勢力に抗してピストン１２０が図中上方に移動する。すると、圧力調整弁の開度が小さくなり、デリバリパイプ内への気体燃料の流出量が少なくなる。 In such a pressure regulating valve, when the fuel pressure in the delivery pipe decreases, the pressure in the pressure regulating chamber 160 communicating with the inside of the delivery pipe decreases, and the piston 120 moves downward in the figure. Then, the opening degree of the pressure regulating valve increases, and the amount of gaseous fuel flowing into the delivery pipe increases. On the other hand, when the fuel pressure in the delivery pipe increases, the pressure in the pressure regulating chamber 160 increases and the piston 120 moves upward in the figure against the urging force from the spring 130. Then, the opening degree of the pressure regulating valve is reduced, and the amount of gaseous fuel flowing into the delivery pipe is reduced.
ところで、噴射弁から気体燃料が噴射されると、デリバリパイプ内の燃料圧力が低下するものの、この低下分を補うように圧力調整弁を通じて気体燃料がデリバリパイプ内に供給される。そのため、噴射弁が間欠的に駆動しているときには、デリバリパイプ内では気体燃料の圧力脈動が発生し、同デリバリパイプ内と連通する調圧室１６０内でも気体燃料の圧力脈動が発生することとなる。こうした気体燃料の圧力脈動は、図８に実線の矢印で示すように、調圧室１６０を区画形成するピストン１２０、同ピストン１２０に接触しているスプリング１３０、同スプリング１３０を支持しているばね受け部材１４０、同ばね受け部材１４０を支持している調整スクリュ１５０、同調整スクリュ１５０を支持しているハウジング１１０の順に伝わる。 By the way, when the gaseous fuel is injected from the injection valve, the fuel pressure in the delivery pipe decreases, but the gaseous fuel is supplied into the delivery pipe through the pressure adjustment valve so as to compensate for this decrease. For this reason, when the injection valve is driven intermittently, the pressure pulsation of the gaseous fuel is generated in the delivery pipe, and the pressure pulsation of the gaseous fuel is generated in the pressure regulating chamber 160 communicating with the inside of the delivery pipe. Become. The pressure pulsation of the gaseous fuel is caused by the piston 120 that defines the pressure regulating chamber 160, the spring 130 that is in contact with the piston 120, and the spring that supports the spring 130, as indicated by solid arrows in FIG. 8. The receiving member 140, the adjustment screw 150 supporting the spring receiving member 140, and the housing 110 supporting the adjustment screw 150 are transmitted in this order.
ここで、ハウジング１１０は、車体に支持されている。そのため、上記の気体燃料の圧力脈動に基づいた振動がハウジング１１０に伝わり、同ハウジング１１０が振動すると、圧力調整弁を支持する車体も振動してしまう。 Here, the housing 110 is supported by the vehicle body. Therefore, vibration based on the pressure pulsation of the gaseous fuel is transmitted to the housing 110, and when the housing 110 vibrates, the vehicle body that supports the pressure regulating valve also vibrates.
なお、圧力調整弁よりも下流側の流体の圧力脈動に起因してハウジングが振動する事象は、気体燃料を供給する経路に圧力調整弁を設ける場合に限らず、気体燃料以外の他の流体を供給するための供給経路に圧力調整弁を設けた場合でも生じうる。 The phenomenon that the housing vibrates due to the pressure pulsation of the fluid downstream from the pressure regulating valve is not limited to the case where the pressure regulating valve is provided in the path for supplying the gaseous fuel. This may occur even when a pressure regulating valve is provided in the supply path for supply.
本発明の目的は、下流側で発生している流体の圧力脈動に起因するハウジングの振動を抑えることができる圧力調整弁を提供することにある。 An object of the present invention is to provide a pressure regulating valve that can suppress vibration of a housing caused by pressure pulsation of a fluid generated downstream.
上記課題を解決するための圧力調整弁は、有底筒状をなすハウジングと、ハウジング内に配置され、同ハウジングの底壁に近づく方向及び同底壁から離れる方向に移動するピストンと、底壁から離れる方向への付勢力をピストンに付与するスプリングと、スプリングを支持するばね受け部材と、底壁に支持されているとともにばね受け部材を支持する支持部材と、を備え、ピストンが進退移動する方向を軸方向とした場合、同ピストンの軸方向における位置に応じた量の流体を出力する弁を前提としている。この弁において、支持部材よりも径方向外側であって、且つ底壁とばね受け部材との間となる位置には、底壁及びばね受け部材の双方に接触する振動吸収部材が設けられている。 A pressure regulating valve for solving the above problems includes a housing having a bottomed cylindrical shape, a piston that is disposed in the housing and moves in a direction approaching and away from the bottom wall of the housing, and a bottom wall A spring for applying an urging force in a direction away from the piston to the piston, a spring receiving member for supporting the spring, and a supporting member supported by the bottom wall and supporting the spring receiving member, and the piston moves forward and backward When the direction is the axial direction, the valve is assumed to output an amount of fluid corresponding to the position of the piston in the axial direction. In this valve, a vibration absorbing member that is in contact with both the bottom wall and the spring receiving member is provided at a position radially outside the support member and between the bottom wall and the spring receiving member. .
上記の圧力調整弁を流体の供給通路に設けた場合に、同圧力調整弁よりも下流側で流体の圧力脈動が発生すると、当該圧力脈動に起因する振動が圧力調整弁に入力される。
この点、上記の圧力調整弁では、ハウジングの底壁とばね受け部材との間の隙間を埋めるように振動吸収部材が設けられている。そのため、流体の圧力脈動が、ピストン、スプリング、ばね受け部材、支持部材、ハウジングの順に伝わる際に、当該圧力脈動に起因するばね受け部材の振動が振動吸収部材によって減衰される。その結果、支持部材及びハウジングには、当該振動が伝わりにくくなる。したがって、圧力調整弁よりも下流側で発生している流体の圧力脈動に起因するハウジングの振動を抑えることができるようになる。
When the pressure regulating valve is provided in the fluid supply passage and a fluid pressure pulsation occurs downstream of the pressure regulating valve, vibration caused by the pressure pulsation is input to the pressure regulating valve.
In this regard, in the pressure regulating valve described above, the vibration absorbing member is provided so as to fill a gap between the bottom wall of the housing and the spring receiving member. Therefore, when the pressure pulsation of the fluid is transmitted in the order of the piston, the spring, the spring receiving member, the support member, and the housing, the vibration of the spring receiving member due to the pressure pulsation is attenuated by the vibration absorbing member. As a result, it is difficult for the vibration to be transmitted to the support member and the housing. Therefore, the vibration of the housing due to the pressure pulsation of the fluid generated downstream from the pressure regulating valve can be suppressed.
なお、上記圧力調整弁において、振動吸収部材は、環状をなしていることが好ましい。この構成によれば、ばね受け部材がどのような方向に振動する場合であっても、振動吸収部材によってばね受け部材の振動を減衰させることができるようになる。 In the pressure regulating valve, it is preferable that the vibration absorbing member has an annular shape. According to this configuration, even if the spring receiving member vibrates in any direction, the vibration of the spring receiving member can be attenuated by the vibration absorbing member.
また、上記圧力調整弁において、ハウジングの底壁は軸方向におけるピストン側に突出する突出部を有し、当該底壁には、軸方向に貫通するとともに突出部の先端に開口する支持用孔を設けてもよい。そして、支持部材は、その先端が支持用孔からピストン側に突出する態様で底壁に支持されていてもよい。また、ばね受け部材は、支持部材の先端に接触するとともに、径方向外側の端部が突出部の先端よりも軸方向において底壁の近くに位置するばね受け本体と、同ばね受け本体の径方向外側の端部に接続され、スプリングを支持する環状のフランジと、を有してもよい。この場合、支持部材の軸方向における位置を調整することにより、スプリングがピストンに付与する付勢力の大きさを変更することができる。このようにピストンへの付勢力を調整することで、圧力調整弁よりも下流側の流体の圧力を調整することができる。 In the pressure regulating valve, the bottom wall of the housing has a protruding portion protruding toward the piston in the axial direction, and the bottom wall has a support hole that penetrates in the axial direction and opens at the tip of the protruding portion. It may be provided. And the support member may be supported by the bottom wall in the aspect which the front-end | tip protrudes from the hole for support to the piston side. The spring receiving member is in contact with the tip of the support member, and has a radially outer end positioned closer to the bottom wall in the axial direction than the tip of the protruding portion, and a diameter of the spring receiving body. And an annular flange that is connected to the outer end of the direction and supports the spring. In this case, the magnitude of the urging force applied by the spring to the piston can be changed by adjusting the position of the support member in the axial direction. By adjusting the urging force applied to the piston in this way, the pressure of the fluid downstream of the pressure adjustment valve can be adjusted.
そして、振動吸収部材を軸方向に延びる筒状部材とし、ハウジングの突出部の外周面と、ばね受け部において同突出部の外周面に対向する面との双方に当該振動吸収部材を接触させるようにすることが好ましい。このように振動吸収部材を筒状とすることにより、支持部材の軸方向における位置がどのような位置であったとしても、振動吸収部材とばね受け部材との接触を維持することができる。すなわち、振動吸収部材によるばね受け部材の振動の減衰効果を確実に発揮させることができるようになる。 The vibration absorbing member is a cylindrical member extending in the axial direction, and the vibration absorbing member is brought into contact with both the outer peripheral surface of the protruding portion of the housing and the surface of the spring receiving portion facing the outer peripheral surface of the protruding portion. It is preferable to make it. Thus, by making the vibration absorbing member cylindrical, contact between the vibration absorbing member and the spring receiving member can be maintained regardless of the position of the support member in the axial direction. That is, the vibration damping effect of the spring receiving member by the vibration absorbing member can be surely exhibited.
ちなみに、振動吸収部材は、径方向における幅が広い肉厚部と、径方向における幅が同肉厚部よりも狭い肉薄部とが軸方向に並んだ構成としてもよい。この場合、肉厚部は、ハウジングの突出部とばね受け部材のばね受け本体との双方に接触し、肉薄部は、ハウジングの突出部及びばね受け本体の何れか一方のみに接触していることが好ましい。 Incidentally, the vibration absorbing member may have a configuration in which a thick portion having a wide width in the radial direction and a thin portion having a narrow width in the radial direction are narrower than the same thick portion. In this case, the thick portion is in contact with both the protruding portion of the housing and the spring receiving body of the spring receiving member, and the thin portion is in contact with only one of the protruding portion of the housing and the spring receiving body. Is preferred.
上記構成によれば、肉薄部をハウジングの突出部にのみ接触させるようにした場合、ばね受け部材における振動吸収部材との接触部分を小さくすることができる。その結果、振動吸収部材のばね受け部材への組み付けの容易性を高めることができる。 According to the said structure, when a thin part is made to contact only the protrusion part of a housing, a contact part with the vibration-absorbing member in a spring receiving member can be made small. As a result, the ease of assembling the vibration absorbing member to the spring receiving member can be enhanced.
反対に、肉薄部をばね受け部材のばね受け本体にのみ接触させるようにした場合、ハウジングの突出部における振動吸収部材との接触部分を小さくすることができる。その結果、振動吸収部材の当該突出部への組み付けの容易性を高めることができる。 On the contrary, when the thin portion is brought into contact only with the spring receiving body of the spring receiving member, the contact portion with the vibration absorbing member at the protruding portion of the housing can be reduced. As a result, the ease of assembling the vibration absorbing member to the protruding portion can be enhanced.
例えば、振動吸収部材は、少なくとも２つの肉厚部を有し、軸方向に沿って肉厚部と肉薄部とが交互に配置された構成とすることが好ましい。この構成によれば、肉薄部をハウジングの突出部にのみ接触させるようにした場合、肉厚部が１つであるときと比較し、振動吸収部材とばね受け部材との接触面積が狭くなりすぎることを抑制することができる。その結果、ばね受け部材の振動を振動吸収部材によって適切に減衰させることができるようになる。 For example, it is preferable that the vibration absorbing member has at least two thick portions, and the thick portions and the thin portions are alternately arranged along the axial direction. According to this configuration, when the thin portion is brought into contact with only the protruding portion of the housing, the contact area between the vibration absorbing member and the spring receiving member is too narrow compared to when the single thick portion is provided. This can be suppressed. As a result, the vibration of the spring receiving member can be appropriately damped by the vibration absorbing member.
反対に、肉薄部をばね受け部材のばね受け本体にのみ接触させるようにした場合、肉厚部が１つであるときと比較し、振動吸収部材とハウジングの突出部との接触面積が狭くなりすぎることを抑制することができる。その結果、ばね受け部材の振動を振動吸収部材によって適切に減衰させることができるようになる。 On the contrary, when the thin portion is made to contact only the spring receiving body of the spring receiving member, the contact area between the vibration absorbing member and the protruding portion of the housing becomes narrower than when the single thick portion is provided. Too much can be suppressed. As a result, the vibration of the spring receiving member can be appropriately damped by the vibration absorbing member.
ところで、上記圧力調整弁において、ばね受け部材は、支持部材の先端に接触するばね受け本体と、同ばね受け本体の径方向外側の端部に接続され、スプリングを支持する環状のフランジと、を有してもよい。また、振動吸収部材は、円盤状をなすとともに、ハウジングの底壁とばね受け部材のフランジとの間に配置されていてもよい。この場合、振動吸収部材の外径をスプリングの外径以上とし、振動吸収部材の内径をスプリングの内径以下とすることが好ましい。この構成によれば、スプリングの軸方向への伸縮を伴うばね受け部材の振動を振動吸収部材によって好適に減衰させることができるようになる。 By the way, in the pressure adjusting valve, the spring receiving member includes: a spring receiving body that contacts the tip of the supporting member; and an annular flange that is connected to a radially outer end of the spring receiving body and supports the spring. You may have. Further, the vibration absorbing member may have a disk shape and be disposed between the bottom wall of the housing and the flange of the spring receiving member. In this case, it is preferable that the outer diameter of the vibration absorbing member is equal to or larger than the outer diameter of the spring, and the inner diameter of the vibration absorbing member is equal to or smaller than the inner diameter of the spring. According to this structure, the vibration of the spring receiving member accompanying expansion and contraction of the spring in the axial direction can be suitably damped by the vibration absorbing member.
ちなみに、グリースなどの液体を樹脂製の袋内に封入した構成のものを振動吸収部材として採用することも可能である。しかし、この場合、樹脂製の袋が破損した際には当該袋から液体が漏出し、ばね受け部材の振動の減衰効果が低下してしまうおそれがある。そこで、上記圧力調整弁において、振動吸収部材を、樹脂によって構成することが好ましい。この構成によれば、振動吸収部材の耐性を高くすることができる。そのため、振動吸収部材の破損に起因してばね受け部材の振動の減衰効果が低下する事象を生じさせにくくすることができる。 Incidentally, a configuration in which a liquid such as grease is enclosed in a resin bag can be employed as the vibration absorbing member. However, in this case, when the resin bag is damaged, liquid leaks from the bag, and the vibration damping effect of the spring receiving member may be reduced. Therefore, in the pressure regulating valve, it is preferable that the vibration absorbing member is made of resin. According to this configuration, the resistance of the vibration absorbing member can be increased. Therefore, it is possible to make it difficult to cause an event in which the vibration damping effect of the spring receiving member is reduced due to the damage of the vibration absorbing member.
（第１の実施形態）
以下、圧力調整弁を具体化した一実施形態を図１〜図４に従って説明する。
図１には、本実施形態の圧力調整弁１０が図示されている。この圧力調整弁１０は、気体燃料の一例であるＣＮＧ（圧縮天然ガス）を内燃機関に供給するための供給経路に設けられている。すなわち、圧力調整弁１０から出力されたＣＮＧは、デリバリパイプ内で一時的に貯留され、噴射弁の駆動によって吸気通路内に供給される。
(First embodiment)
Hereinafter, an embodiment embodying a pressure regulating valve will be described with reference to FIGS.
FIG. 1 illustrates a pressure regulating valve 10 of the present embodiment. The pressure regulating valve 10 is provided in a supply path for supplying CNG (compressed natural gas), which is an example of gaseous fuel, to the internal combustion engine. That is, CNG output from the pressure regulating valve 10 is temporarily stored in the delivery pipe and supplied into the intake passage by driving the injection valve.
図１に示すように、圧力調整弁１０の圧力調整部２０は、ボディ２１と、ボディ２１の図中上部に固定されている有底筒状のハウジング２２とを備えている。このハウジング２２には、図中上下方向である軸方向Ｚにおける一端及び他端の双方に開口する筒体２３と、筒体２３の軸方向Ｚにおける一端である図中上端の開口を閉塞する蓋体２４とが設けられている。すなわち、本実施形態の圧力調整弁１０では、蓋体２４により、「ハウジング２２の底壁」の一例が構成されている。なお、筒体２３の軸方向Ｚにおける他端である図中下端の開口は、ボディ２１によって閉塞されている。 As shown in FIG. 1, the pressure adjustment unit 20 of the pressure adjustment valve 10 includes a body 21 and a bottomed cylindrical housing 22 fixed to the upper portion of the body 21 in the figure. The housing 22 has a cylindrical body 23 that opens at both one end and the other end in the axial direction Z that is the vertical direction in the figure, and a lid that closes the opening at the upper end in the figure that is one end in the axial direction Z of the cylindrical body 23. A body 24 is provided. In other words, in the pressure regulating valve 10 of the present embodiment, the lid body 24 constitutes an example of “the bottom wall of the housing 22”. Note that the opening at the lower end in the figure, which is the other end in the axial direction Z of the cylindrical body 23, is closed by the body 21.
本実施形態の圧力調整弁１０は、ＣＮＧからオイルなどの異物を分離させるオイルセパレータ１１を備えている。このオイルセパレータ１１は、ボディ２１の図中下部に固定されており、圧力調整部２０によって規定圧に減圧されたＣＮＧから異物を分離するようになっている。そして、オイルセパレータ１１によって異物を分離した後の同ＣＮＧが圧力調整弁１０よりも下流、すなわちデリバリパイプ内に供給されるようになっている。 The pressure regulating valve 10 of the present embodiment includes an oil separator 11 that separates foreign substances such as oil from CNG. The oil separator 11 is fixed to the lower part of the body 21 in the figure, and separates foreign substances from the CNG that has been reduced to a specified pressure by the pressure adjusting unit 20. The CNG after the foreign matter is separated by the oil separator 11 is supplied downstream from the pressure regulating valve 10, that is, into the delivery pipe.
次に、図１及び図２を参照し、圧力調整部２０の構成について説明する。
図１及び図２に示すように、蓋体２４は、軸方向Ｚにおけるボディ２１側となる図中下方に突出する突出部２４１を有している。また、蓋体２４には、軸方向Ｚに延びる支持用孔２４２が設けられている。この支持用孔２４２は、蓋体２４の図中上面に開口するとともに、突出部２４１の先端面である図中下面に開口している。すなわち、突出部２４１は、円筒形状をなしている。そして、蓋体２４は、この支持用孔２４２を通じて支持部材としての調整スクリュ２５を支持している。この調整スクリュ２５の図中上部である基端は支持用孔２４２内に位置しており、調整スクリュ２５の先端は、支持用孔２４２の図中下方の開口からボディ２１側に突出している。なお、調整スクリュ２５は、支持用孔２４２内に螺合されており、調整スクリュ２５の先端の軸方向Ｚにおける位置は調整可能である。
Next, the configuration of the pressure adjusting unit 20 will be described with reference to FIGS. 1 and 2.
As shown in FIGS. 1 and 2, the lid body 24 has a protruding portion 241 that protrudes downward in the drawing on the body 21 side in the axial direction Z. The lid 24 is provided with a support hole 242 extending in the axial direction Z. The support hole 242 opens in the upper surface of the lid 24 in the figure, and also opens in the lower surface in the figure, which is the tip surface of the protrusion 241. That is, the protrusion 241 has a cylindrical shape. The lid 24 supports the adjustment screw 25 as a support member through the support hole 242. The base end, which is the upper part of the adjustment screw 25 in the figure, is located in the support hole 242, and the tip of the adjustment screw 25 protrudes from the lower opening of the support hole 242 in the figure to the body 21 side. The adjustment screw 25 is screwed into the support hole 242, and the position of the tip of the adjustment screw 25 in the axial direction Z can be adjusted.
また、ハウジング２２内には、調整スクリュ２５の先端で支持されているばね受け部材２６が設けられている。このばね受け部材２６には、調整スクリュ２５の先端に接触しているばね受け本体２６１と、ばね受け本体２６１の径方向外側の端部に接続されている円環状のフランジ２６３とが設けられている。ばね受け本体２６１の径方向外側の端部は、軸方向Ｚにおいて蓋体２４の突出部２４１の基端と先端との間、すなわち突出部２４１の図中上端と図中下端との間に位置している。そのため、ばね受け本体２６１の径方向外側の端部に接続されているフランジ２６３もまた、軸方向Ｚにおいて蓋体２４の突出部２４１の基端と先端との間に位置している。 In addition, a spring receiving member 26 supported at the tip of the adjustment screw 25 is provided in the housing 22. The spring receiving member 26 is provided with a spring receiving body 261 that is in contact with the tip of the adjustment screw 25 and an annular flange 263 that is connected to the radially outer end of the spring receiving body 261. Yes. The radially outer end of the spring receiver main body 261 is positioned between the base end and the distal end of the protruding portion 241 of the lid body 24 in the axial direction Z, that is, between the upper end in the drawing and the lower end in the drawing. doing. Therefore, the flange 263 connected to the end portion on the radially outer side of the spring receiving body 261 is also positioned between the proximal end and the distal end of the protruding portion 241 of the lid body 24 in the axial direction Z.
こうしたばね受け本体２６１は、フランジ２６３の径方向内側の端部に接続されている円筒形状の筒状部分２６２を有している。この筒状部分２６２の内径は、蓋体２４の突出部２４１の外径よりも大きい。そして、本実施形態の圧力調整弁１０では、ばね受け部材２６の筒状部分２６２と蓋体２４の突出部２４１との間に、筒状部分２６２と突出部２４１との間の隙間を埋めるように振動吸収部材６０が設けられている。この振動吸収部材６０は、突出部２４１の外周面と、筒状部分２６２において突出部２４１の外周面に対向する面との双方に密接（接触）している。なお、振動吸収部材６０の構成については後述する。 Such a spring receiving body 261 has a cylindrical tubular portion 262 connected to the radially inner end of the flange 263. The inner diameter of the cylindrical portion 262 is larger than the outer diameter of the protruding portion 241 of the lid body 24. In the pressure regulating valve 10 of the present embodiment, the gap between the cylindrical portion 262 and the protruding portion 241 is filled between the cylindrical portion 262 of the spring receiving member 26 and the protruding portion 241 of the lid 24. A vibration absorbing member 60 is provided on the surface. The vibration absorbing member 60 is in close contact (contact) with both the outer peripheral surface of the protruding portion 241 and the surface of the cylindrical portion 262 that faces the outer peripheral surface of the protruding portion 241. The configuration of the vibration absorbing member 60 will be described later.
また、ハウジング２２内には、筒体２３に沿って軸方向Ｚに摺動（移動）するピストン２７と、ハウジング２２の蓋体２４から離れる方向である図中下方への付勢力をピストン２７に付与する調圧用スプリング２８とが設けられている。この調圧用スプリング２８の軸方向Ｚにおける一端である図中上端が、ばね受け部材２６のフランジ２６３によって支持されている。 Further, in the housing 22, a piston 27 that slides (moves) in the axial direction Z along the cylindrical body 23 and a downward biasing force in the figure, which is a direction away from the lid body 24 of the housing 22, are applied to the piston 27. A pressure adjusting spring 28 is provided. The upper end in the figure, which is one end of the pressure adjusting spring 28 in the axial direction Z, is supported by the flange 263 of the spring receiving member 26.
なお、ピストン２７とボディ２１との間に形成されている空間が、高圧のＣＮＧを規定圧に減圧させる調圧室２９となっている。この調圧室２９内はオイルセパレータ１１を通じて上記デリバリパイプ内と連通しており、調圧室２９内の圧力は、上記デリバリパイプ内の燃料圧力に応じた圧力となる。そして、デリバリパイプ内の燃料圧力が低いときには、調圧室２９内の圧力が低くなり、結果として、ピストン２７が軸方向Ｚにおいてボディ２１の近くに位置するようになる。一方、デリバリパイプ内の燃料圧力が高いときには、調圧室２９内の圧力が高くなり、結果として、ピストン２７が軸方向Ｚにおいてボディ２１から離れた位置に位置するようになる。 A space formed between the piston 27 and the body 21 serves as a pressure regulating chamber 29 for reducing the high-pressure CNG to a specified pressure. The pressure regulating chamber 29 communicates with the delivery pipe through the oil separator 11, and the pressure in the pressure regulating chamber 29 is a pressure corresponding to the fuel pressure in the delivery pipe. When the fuel pressure in the delivery pipe is low, the pressure in the pressure regulating chamber 29 is low, and as a result, the piston 27 is positioned near the body 21 in the axial direction Z. On the other hand, when the fuel pressure in the delivery pipe is high, the pressure in the pressure regulating chamber 29 is high, and as a result, the piston 27 is located at a position away from the body 21 in the axial direction Z.
ボディ２１内には、燃料タンクから供給される高圧のＣＮＧが流入する弁室４０が設けられている。また、ボディ２１において弁室４０よりも図中上側には、ボディ２１の図中上面に開口し、弁室４０よりも大径の中間部４１が設けられている。この中間部４１内には、弁室４０と調圧室２９とを区画する区画部材４２が設けられている。この区画部材４２には、軸方向Ｚに貫通するとともに、弁室４０内と調圧室２９内とを連通させる連通孔４２１が設けられている。 A valve chamber 40 into which high-pressure CNG supplied from the fuel tank flows is provided in the body 21. In the body 21, an intermediate portion 41 that opens to the upper surface of the body 21 in the drawing and has a larger diameter than the valve chamber 40 is provided above the valve chamber 40 in the drawing. A partition member 42 that partitions the valve chamber 40 and the pressure regulating chamber 29 is provided in the intermediate portion 41. The partition member 42 is provided with a communication hole 421 that penetrates in the axial direction Z and communicates the inside of the valve chamber 40 and the pressure regulating chamber 29.
圧力調整部２０の弁体４３は、弁室４０内に位置する本体部４３１と、本体部４３１から連通孔４２１を通じて調圧室２９内まで延びているロッド部４３２とを有している。そして、本体部４３１が位置する弁室４０内には、本体部４３１を区画部材４２に向けて付勢する弁室スプリング４４が設けられている。 The valve body 43 of the pressure adjusting unit 20 includes a main body portion 431 located in the valve chamber 40 and a rod portion 432 extending from the main body portion 431 through the communication hole 421 into the pressure regulating chamber 29. A valve chamber spring 44 that urges the main body 431 toward the partition member 42 is provided in the valve chamber 40 where the main body 431 is located.
ロッド部４３２と、区画部材４２における連通孔４２１の周壁との間には、弁室４０内から調圧室２９内にＣＮＧを流動させる連通路が設けられている。弁体４３の本体部４３１が区画部材４２に着座しているときには、連通路が弁体４３の本体部４３１によって閉塞され、弁室４０内から調圧室２９内にＣＮＧが流れない。一方、弁体４３の本体部４３１が区画部材４２から図中下方に離れているときには、連通路を通じて弁室４０内から調圧室２９内にＣＮＧが流れるようになっている。 Between the rod portion 432 and the peripheral wall of the communication hole 421 in the partition member 42, a communication path is provided for allowing CNG to flow from the valve chamber 40 into the pressure regulating chamber 29. When the main body portion 431 of the valve body 43 is seated on the partition member 42, the communication path is blocked by the main body portion 431 of the valve body 43, and CNG does not flow from the valve chamber 40 into the pressure regulating chamber 29. On the other hand, when the main body 431 of the valve body 43 is separated downward from the partition member 42 in the figure, CNG flows from the valve chamber 40 into the pressure regulating chamber 29 through the communication path.
なお、ロッド部４３２の先端は、連結部材４６を通じてピストン２７に連結されている。そのため、ピストン２７が図中下方に摺動しているときには弁体４３もまた図中下方に移動する一方、ピストン２７が図中上方に摺動しているときには弁体４３もまた図中上方に移動するようになっている。ただし、弁体４３の本体部４３１が区画部材４２に着座し、連通孔４２１の開口が閉塞されると、ピストン２７は図中上方に摺動しない。すなわち、圧力調整部２０の開度は、ピストン２７の軸方向Ｚにおける位置に応じた開度となる。例えば、ピストン２７が図中下方に摺動し、圧力調整部２０の開度が大きくなると、圧力調整部２０から出力されるＣＮＧの量が多くなる。 The tip of the rod part 432 is connected to the piston 27 through the connecting member 46. Therefore, when the piston 27 slides downward in the figure, the valve element 43 also moves downward in the figure, while when the piston 27 slides upward in the figure, the valve element 43 also moves upward in the figure. It is supposed to move. However, when the main body 431 of the valve body 43 is seated on the partition member 42 and the opening of the communication hole 421 is closed, the piston 27 does not slide upward in the drawing. That is, the opening degree of the pressure adjusting unit 20 is an opening degree corresponding to the position of the piston 27 in the axial direction Z. For example, when the piston 27 slides downward in the drawing and the opening degree of the pressure adjusting unit 20 increases, the amount of CNG output from the pressure adjusting unit 20 increases.
次に、図３を参照し、振動吸収部材６０の構成について説明する。
図３に示すように、振動吸収部材６０は、軸方向Ｚに延びる円筒形状をなしており、シリコーンなどの樹脂によって構成されている。この振動吸収部材６０は、径方向における幅の広い肉厚部６１と、径方向における幅が肉厚部６１よりも狭い肉薄部６２とが軸方向Ｚに並んだ構成となっている。本実施形態の圧力調整弁１０では、振動吸収部材６０は、複数（図３に示す例では３つ）の肉厚部６１を有しており、軸方向Ｚに沿って肉厚部６１と肉薄部６２とが交互に配置された構成となっている。なお、本明細書では、径方向内側の端部から径方向外側の端部までの距離が長いことを「径方向における幅が広い」といい、径方向内側の端部から径方向外側の端部までの距離が短いことを「径方向における幅が狭い」というものとする。
Next, the configuration of the vibration absorbing member 60 will be described with reference to FIG.
As shown in FIG. 3, the vibration absorbing member 60 has a cylindrical shape extending in the axial direction Z, and is made of a resin such as silicone. The vibration absorbing member 60 has a configuration in which a thick portion 61 having a wide width in the radial direction and a thin portion 62 having a narrow width in the radial direction smaller than the thick portion 61 are arranged in the axial direction Z. In the pressure regulating valve 10 of the present embodiment, the vibration absorbing member 60 has a plurality (three in the example shown in FIG. 3) thick portions 61, and the thick portions 61 and the thin portions along the axial direction Z. The parts 62 are arranged alternately. In the present specification, a long distance from the radially inner end to the radially outer end is referred to as “the width in the radial direction is wide”, and the radially outer end from the radially inner end. The short distance to the part is referred to as “the width in the radial direction is narrow”.
また、振動吸収部材６０にあっては、肉薄部６２の内径が肉厚部６１の内径と等しい一方で、肉薄部６２の外径が肉厚部６１の外径よりも小さい。すなわち、本振動吸収部材６０は、軸方向Ｚにおいて互いに異なる位置に複数の環状のリブが並んだ構成であるということもできる。 In the vibration absorbing member 60, the inner diameter of the thin portion 62 is equal to the inner diameter of the thick portion 61, while the outer diameter of the thin portion 62 is smaller than the outer diameter of the thick portion 61. That is, it can also be said that the vibration absorbing member 60 has a configuration in which a plurality of annular ribs are arranged at different positions in the axial direction Z.
そして、こうした振動吸収部材６０の内周面は、蓋体２４の突出部２４１の外周面に密接（接触）している。すなわち、肉厚部６１及び肉薄部６２の双方の径方向内側の端部が突出部２４１の外周面に密接している。また、振動吸収部材６０の外周側にあっては、各肉厚部６１の径方向外側の端部がばね受け部材２６の筒状部分２６２の内周面に密接（接触）する一方で、各肉薄部６２の径方向外側の端部は筒状部分２６２から離れている。すなわち、肉薄部６２の径方向外側の端部は、筒状部分２６２の内周面よりも径方向内側に位置しており、肉薄部６２の径方向外側の端部と筒状部分２６２の内周面との間には隙間が介在している。 The inner peripheral surface of the vibration absorbing member 60 is in close contact (contact) with the outer peripheral surface of the protruding portion 241 of the lid body 24. That is, the radially inner ends of both the thick portion 61 and the thin portion 62 are in close contact with the outer peripheral surface of the protruding portion 241. Further, on the outer peripheral side of the vibration absorbing member 60, the radially outer end of each thick portion 61 is in close contact (contact) with the inner peripheral surface of the cylindrical portion 262 of the spring receiving member 26, The radially outer end of the thin portion 62 is separated from the cylindrical portion 262. That is, the radially outer end of the thin portion 62 is positioned radially inward of the inner peripheral surface of the tubular portion 262, and the radially outer end of the thin portion 62 and the inner portion of the tubular portion 262 are located inside. A gap is interposed between the peripheral surface.
次に、図４を参照し、ハウジング２２に振動吸収部材６０及びばね受け部材２６を組み付ける際の手順について説明する。
図４（ａ）に示すように、蓋体２４の突出部２４１に振動吸収部材６０が装着される。これにより、振動吸収部材６０の内周面が突出部２４１の外周面に密接する。そして、図４（ｂ）に示すように、この状態で蓋体２４へのばね受け部材２６の装着が行われる。振動吸収部材６０は、蓋体２４の突出部２４１及びばね受け部材２６の筒状部分２６２の双方に密接する肉厚部６１だけではなく、筒状部分２６２には接触しない肉薄部６２を有する構成となっている。そのため、振動吸収部材６０が肉薄部６２を有しない構成の場合と比較し、振動吸収部材６０における筒状部分２６２との接触部分が狭くなる。すなわち、ばね受け部材２６を装着する際の摺動抵抗が小さくなる。したがって、ばね受け部材２６を蓋体２４に装着する際の容易性が高くなっている。
Next, a procedure for assembling the vibration absorbing member 60 and the spring receiving member 26 to the housing 22 will be described with reference to FIG.
As shown in FIG. 4A, the vibration absorbing member 60 is attached to the protruding portion 241 of the lid body 24. Thereby, the inner peripheral surface of the vibration absorbing member 60 is in close contact with the outer peripheral surface of the protruding portion 241. Then, as shown in FIG. 4B, the spring receiving member 26 is attached to the lid 24 in this state. The vibration absorbing member 60 includes not only the thick portion 61 that is in close contact with both the protruding portion 241 of the lid 24 and the cylindrical portion 262 of the spring receiving member 26, but also the thin portion 62 that does not contact the cylindrical portion 262. It has become. Therefore, compared with the case where the vibration absorbing member 60 does not have the thin portion 62, the contact portion with the cylindrical portion 262 in the vibration absorbing member 60 is narrowed. That is, the sliding resistance when mounting the spring receiving member 26 is reduced. Therefore, the ease of attaching the spring receiving member 26 to the lid 24 is increased.
次に、本実施形態の圧力調整弁１０の作用について説明する。
上記噴射弁からＣＮＧが間欠的に噴射されると、デリバリパイプ内ではＣＮＧの圧力脈動が発生する。このように圧力調整弁１０よりも下流でＣＮＧの圧力脈動が発生すると、圧力調整部２０の調圧室２９でもＣＮＧの圧力が脈動するようになる。その結果、こうした圧力脈動が、ピストン２７、調圧用スプリング２８、ばね受け部材２６、調整スクリュ２５、ハウジング２２の蓋体２４の順に伝達される。
Next, the operation of the pressure regulating valve 10 of this embodiment will be described.
When CNG is intermittently injected from the injection valve, pressure pulsation of CNG occurs in the delivery pipe. Thus, when the CNG pressure pulsation occurs downstream of the pressure regulating valve 10, the CNG pressure also pulsates in the pressure regulating chamber 29 of the pressure regulating unit 20. As a result, such pressure pulsation is transmitted in the order of the piston 27, the pressure adjusting spring 28, the spring receiving member 26, the adjusting screw 25, and the lid 24 of the housing 22.
本実施形態の圧力調整弁１０では、ばね受け部材２６の筒状部分２６２と蓋体２４の突出部２４１との間に振動吸収部材６０が設けられている。この振動吸収部材６０は筒状部分２６２及び突出部２４１の双方に密接しているため、ばね受け部材２６は径方向及び軸方向Ｚに変位しにくくなる。その結果、上記の圧力脈動に起因してばね受け部材２６が振動しても、当該ばね受け部材２６の振動が振動吸収部材６０によって減衰される。これにより、振動吸収部材６０によって減衰された振動が、調整スクリュ２５及びハウジング２２に伝わることとなる。すなわち、ハウジング２２には上記の圧力脈動に起因する振動があまり伝達されなくなり、振動吸収部材６０を設けない場合と比較し、ハウジング２２の振動が小さくなる。 In the pressure regulating valve 10 of the present embodiment, the vibration absorbing member 60 is provided between the cylindrical portion 262 of the spring receiving member 26 and the protruding portion 241 of the lid 24. Since the vibration absorbing member 60 is in close contact with both the cylindrical portion 262 and the protruding portion 241, the spring receiving member 26 is difficult to be displaced in the radial direction and the axial direction Z. As a result, even if the spring receiving member 26 vibrates due to the pressure pulsation, the vibration of the spring receiving member 26 is attenuated by the vibration absorbing member 60. Thereby, the vibration attenuated by the vibration absorbing member 60 is transmitted to the adjustment screw 25 and the housing 22. That is, the vibration due to the pressure pulsation is not transmitted to the housing 22 so much, and the vibration of the housing 22 is reduced as compared with the case where the vibration absorbing member 60 is not provided.
ここで、圧力調整弁１０のハウジング２２は、車体に支持されている。そのため、ハウジング２２の振動が大きいと、当該振動が車体に伝わりやすくなり、車両の乗員が不快を覚えやすい。しかし、本実施形態の圧力調整弁１０では、振動吸収部材６０を設けることにより、ハウジング２２が振動しにくくなっている。そのため、ハウジング２２を介して車体に伝達される振動も小さくなる。 Here, the housing 22 of the pressure regulating valve 10 is supported by the vehicle body. Therefore, if the vibration of the housing 22 is large, the vibration is easily transmitted to the vehicle body, and the vehicle occupant is likely to feel uncomfortable. However, in the pressure regulating valve 10 of the present embodiment, the housing 22 is less likely to vibrate by providing the vibration absorbing member 60. For this reason, vibration transmitted to the vehicle body via the housing 22 is also reduced.
以上、上記構成及び作用によれば、以下に示す効果を得ることができる。
（１）ハウジング２２の蓋体２４とばね受け部材２６との間の隙間を埋めるように振動吸収部材６０が設けられている。そのため、ＣＮＧの圧力脈動が、ピストン２７、調圧用スプリング２８、ばね受け部材２６、調整スクリュ２５、ハウジング２２の順に伝わる際に、上記の圧力脈動に起因するばね受け部材２６の振動が振動吸収部材６０によって減衰される。その結果、調整スクリュ２５及びハウジング２２には、当該振動が伝わりにくくなる。したがって、圧力調整弁１０よりも下流側で発生しているＣＮＧの圧力脈動に起因するハウジング２２の振動を抑えることができる。
As mentioned above, according to the said structure and effect | action, the effect shown below can be acquired.
(1) A vibration absorbing member 60 is provided so as to fill a gap between the lid 24 of the housing 22 and the spring receiving member 26. Therefore, when the pressure pulsation of the CNG is transmitted in the order of the piston 27, the pressure adjusting spring 28, the spring receiving member 26, the adjusting screw 25, and the housing 22, the vibration of the spring receiving member 26 caused by the pressure pulsation is a vibration absorbing member. Attenuated by 60. As a result, the vibration is hardly transmitted to the adjustment screw 25 and the housing 22. Therefore, the vibration of the housing 22 caused by the pressure pulsation of CNG generated downstream of the pressure regulating valve 10 can be suppressed.
（２）振動吸収部材６０は、環状をなしている。そのため、ばね受け部材２６がどのような方向に振動する場合であっても、振動吸収部材６０によってばね受け部材２６の振動を減衰させることができる。 (2) The vibration absorbing member 60 has an annular shape. Therefore, even if the spring receiving member 26 vibrates in any direction, the vibration of the spring receiving member 26 can be attenuated by the vibration absorbing member 60.
（３）より具体的には、振動吸収部材６０は、軸方向Ｚに延びる筒状部材である。そのため、調整スクリュ２５による調整によってばね受け部材２６の軸方向Ｚにおける位置が変わったとしても、振動吸収部材６０とばね受け部材２６との密接を維持することができる。すなわち、振動吸収部材６０によるばね受け部材２６の振動の減衰効果を確実に発揮させることができる。 (3) More specifically, the vibration absorbing member 60 is a cylindrical member extending in the axial direction Z. Therefore, even if the position of the spring receiving member 26 in the axial direction Z is changed by the adjustment by the adjustment screw 25, the vibration absorbing member 60 and the spring receiving member 26 can be kept in close contact with each other. That is, the vibration damping effect of the spring receiving member 26 by the vibration absorbing member 60 can be reliably exhibited.
（４）本実施形態の圧力調整弁１０では、肉薄部６２は、蓋体２４の突出部２４１に密接している一方で、ばね受け部材２６の筒状部分２６２には接触していない。そのため、ばね受け部材２６における振動吸収部材６０との接触部分が小さくなっている。すなわち、肉薄部６２を有しない振動吸収部材を採用する場合と比較して、ばね受け部材２６を蓋体２４に装着させる際にばね受け部材２６が受ける摺動抵抗を小さくすることができる。その結果、振動吸収部材６０のばね受け部材２６への組み付けの容易性を高めることができる。 (4) In the pressure regulating valve 10 of the present embodiment, the thin portion 62 is in close contact with the protruding portion 241 of the lid body 24, but is not in contact with the cylindrical portion 262 of the spring receiving member 26. For this reason, the contact portion of the spring receiving member 26 with the vibration absorbing member 60 is small. That is, the sliding resistance received by the spring receiving member 26 when the spring receiving member 26 is attached to the lid 24 can be reduced as compared with the case where the vibration absorbing member having no thin portion 62 is employed. As a result, the ease of assembling the vibration absorbing member 60 to the spring receiving member 26 can be enhanced.
（５）また、振動吸収部材６０は、蓋体２４の突出部２４１及びばね受け部材２６の筒状部分２６２の双方に密接する肉厚部６１を複数有している。そのため、肉厚部６１が１つのみであるときと比較し、振動吸収部材６０とばね受け部材２６との接触面積が狭くなりすぎることを抑制することができる。その結果、振動吸収部材６０によるばね受け部材２６の振動を適切に減衰させることができる。 (5) Further, the vibration absorbing member 60 has a plurality of thick portions 61 that are in close contact with both the protruding portion 241 of the lid body 24 and the cylindrical portion 262 of the spring receiving member 26. Therefore, it is possible to suppress the contact area between the vibration absorbing member 60 and the spring receiving member 26 from becoming too narrow as compared with the case where there is only one thick portion 61. As a result, the vibration of the spring receiving member 26 caused by the vibration absorbing member 60 can be appropriately damped.
（６）振動吸収部材として、グリースなどの液体を樹脂製の袋内に封入したものを採用した場合と比較し、振動吸収部材の耐性を高くすることができる。そのため、振動吸収部材の破損に起因してばね受け部材２６の振動の減衰効果が低下する事象を生じさせにくくすることができる。 (6) The resistance of the vibration absorbing member can be increased as compared with a case where a vibration absorbing member in which a liquid such as grease is sealed in a resin bag is employed. Therefore, it is possible to make it difficult to cause an event in which the vibration damping effect of the spring receiving member 26 is reduced due to the damage of the vibration absorbing member.
（第２の実施形態）
次に、圧力調整弁を具体化した第２の実施形態を図５に従って説明する。本実施形態の圧力調整弁では、振動吸収部材の配置位置などが第１の実施形態と相違している。したがって、以下の説明においては、第１の実施形態と相違する部分について主に説明するものとし、第１の実施形態と同一の部材構成には同一符号を付して重複説明を省略するものとする。
(Second Embodiment)
Next, a second embodiment in which the pressure regulating valve is embodied will be described with reference to FIG. In the pressure regulating valve of the present embodiment, the arrangement position of the vibration absorbing member is different from that of the first embodiment. Therefore, in the following description, parts different from those of the first embodiment will be mainly described, and the same member configuration as that of the first embodiment will be denoted by the same reference numerals and redundant description will be omitted. To do.
図５に示すように、本実施形態の圧力調整弁１０では、振動吸収部材６０Ａは、円盤状をなしている。そして、振動吸収部材６０Ａは、ばね受け部材２６のフランジ２６３と蓋体２４との間に配置されている。すなわち、フランジ２６３と蓋体２４との間の隙間が、振動吸収部材６０Ａによって埋められている。このとき、振動吸収部材６０Ａは、フランジ２６３と蓋体２４との双方に密接（接触）している。 As shown in FIG. 5, in the pressure regulating valve 10 of the present embodiment, the vibration absorbing member 60A has a disk shape. The vibration absorbing member 60 </ b> A is disposed between the flange 263 of the spring receiving member 26 and the lid body 24. That is, the gap between the flange 263 and the lid body 24 is filled with the vibration absorbing member 60A. At this time, the vibration absorbing member 60 </ b> A is in close contact (contact) with both the flange 263 and the lid body 24.
図５に示す例では、振動吸収部材６０Ａの外径は、調圧用スプリング２８の外径と等しい。また、振動吸収部材６０Ａの内径は、調圧用スプリング２８の内径よりも小さい。
そして、こうした構成であっても、圧力調整弁１０よりも下流で発生したＣＮＧの圧力脈動がピストン２７及び調圧用スプリング２８を通じてばね受け部材２６に伝達されても、当該ばね受け部材２６の振動が振動吸収部材６０Ａによって好適に減衰される。そのため、上記の圧力脈動に起因するハウジング２２の振動が小さくなる。
In the example shown in FIG. 5, the outer diameter of the vibration absorbing member 60 </ b> A is equal to the outer diameter of the pressure adjusting spring 28. Further, the inner diameter of the vibration absorbing member 60 </ b> A is smaller than the inner diameter of the pressure adjusting spring 28.
Even in such a configuration, even if the pressure pulsation of CNG generated downstream of the pressure regulating valve 10 is transmitted to the spring receiving member 26 through the piston 27 and the pressure adjusting spring 28, the vibration of the spring receiving member 26 is not affected. It is suitably damped by the vibration absorbing member 60A. Therefore, the vibration of the housing 22 due to the pressure pulsation is reduced.
以上、上記構成及び作用によれば、上記第１の実施形態の効果（１），（２）及び（６）と同等の効果に加え、以下に示す効果をさらに得ることができる。
（７）調圧用スプリング２８の軸方向Ｚへの伸縮を伴うばね受け部材２６の振動を振動吸収部材６０Ａによって好適に減衰させることができる。
As mentioned above, according to the said structure and effect | action, in addition to the effect (1) of the said 1st Embodiment, the effect equivalent to (2) and (6), the effect shown below can further be acquired.
(7) The vibration of the spring receiving member 26 accompanying expansion and contraction of the pressure adjusting spring 28 in the axial direction Z can be suitably damped by the vibration absorbing member 60A.
なお、上記各実施形態は以下のような別の実施形態に変更してもよい。
・第１の実施形態において、ばね受け部材２６の筒状部分２６２と蓋体２４の突出部２４１との間に配置されているのであれば、振動吸収部材６０の形状を適宜変更してもよい。例えば、図６に示すように、振動吸収部材６０は、筒状部分２６２に密接（接触）する一方で突出部２４１に接触しない肉薄部６２を有する構成であってもよい。この場合、肉薄部６２を有しない振動吸収部材と比較し、突出部２４１における振動吸収部材６０との接触部分が小さくなる。そのため、振動吸収部材６０をばね受け部材２６に装着させた上で、ばね受け部材２６を蓋体２４に装着させるようにすることが好ましい。この場合、ばね受け部材２６を蓋体２４に装着する際における振動吸収部材６０と突出部２４１との間で発生する摺動抵抗が小さいため、装着の容易性を高めることができる。
In addition, you may change each said embodiment into another embodiment as follows.
-In 1st Embodiment, as long as it arrange | positions between the cylindrical part 262 of the spring receiving member 26, and the protrusion part 241 of the cover body 24, you may change the shape of the vibrational absorption member 60 suitably. . For example, as shown in FIG. 6, the vibration absorbing member 60 may have a thin portion 62 that is in close contact (contact) with the cylindrical portion 262 but does not contact the protruding portion 241. In this case, compared with a vibration absorbing member that does not have the thin portion 62, the contact portion of the protruding portion 241 with the vibration absorbing member 60 is reduced. Therefore, it is preferable that the vibration absorbing member 60 is mounted on the spring receiving member 26 and then the spring receiving member 26 is mounted on the lid 24. In this case, since the sliding resistance generated between the vibration absorbing member 60 and the protruding portion 241 when the spring receiving member 26 is mounted on the lid 24 is small, the mounting ease can be improved.
また、こうした構成であっても、振動吸収部材６０は、複数の肉厚部６１を有している。そのため、蓋体２４の突出部２４１と振動吸収部材６０との接触面積が狭くなりすぎることを抑制することができる。その結果、ばね受け部材２６の振動を振動吸収部材６０によって適切に減衰させることができる。 Even with such a configuration, the vibration absorbing member 60 has a plurality of thick portions 61. Therefore, it is possible to prevent the contact area between the protrusion 241 of the lid body 24 and the vibration absorbing member 60 from becoming too narrow. As a result, the vibration of the spring receiving member 26 can be appropriately damped by the vibration absorbing member 60.
・第１の実施形態において、振動吸収部材６０は、ばね受け部材２６の筒状部分２６２と蓋体２４の突出部２４１との双方に肉薄部６２が接触しない構成であってもよい。この場合、肉薄部６２の内径は肉厚部６１の内径よりも大きく、肉薄部６２の外径は肉厚部６１の外径よりも小さくなることとなる。 In the first embodiment, the vibration absorbing member 60 may be configured such that the thin portion 62 does not contact both the cylindrical portion 262 of the spring receiving member 26 and the protruding portion 241 of the lid 24. In this case, the inner diameter of the thin portion 62 is larger than the inner diameter of the thick portion 61, and the outer diameter of the thin portion 62 is smaller than the outer diameter of the thick portion 61.
・第１の実施形態において、振動吸収部材６０は、円筒形状をなす部材本体と、同部材本体から径方向外側に突出する突起及び径方向内側に突出する突起のうち少なくとも一方を有する構成であってもよい。 In the first embodiment, the vibration absorbing member 60 is configured to include at least one of a cylindrical member main body, a protrusion protruding radially outward from the member main body, and a protrusion protruding radially inward. May be.
・第１の実施形態において、ばね受け部材２６の筒状部分２６２と蓋体２４の突出部２４１との間に配置することができるのであれば、環状ではない部材を振動吸収部材６０として採用してもよい。例えば、軸方向Ｚに延びる短冊状の振動吸収部材６０を、周方向に沿って配置するようにしてもよい。 -In 1st Embodiment, if it can arrange | position between the cylindrical part 262 of the spring receiving member 26, and the protrusion part 241 of the cover body 24, the member which is not cyclic | annular will be employ | adopted as the vibration absorption member 60. FIG. May be. For example, the strip-shaped vibration absorbing member 60 extending in the axial direction Z may be arranged along the circumferential direction.
・第２の実施形態において、振動吸収部材６０Ａの形状を適宜変更してもよい。例えば、図７に示すように、振動吸収部材６０Ａの外径を、調圧用スプリング２８の外径よりも大きくしてもよい。また、振動吸収部材６０Ａの内径を、ばね受け部材２６の筒状部分２６２の内径よりも小さくしてもよい。また、振動吸収部材６０Ａの内径を、調圧用スプリング２８の内径と等しくしてもよい。 In the second embodiment, the shape of the vibration absorbing member 60A may be changed as appropriate. For example, as shown in FIG. 7, the outer diameter of the vibration absorbing member 60 </ b> A may be larger than the outer diameter of the pressure adjusting spring 28. Further, the inner diameter of the vibration absorbing member 60 </ b> A may be smaller than the inner diameter of the cylindrical portion 262 of the spring receiving member 26. Further, the inner diameter of the vibration absorbing member 60 </ b> A may be equal to the inner diameter of the pressure adjusting spring 28.
・第２の実施形態において、ばね受け部材２６のフランジ２６３と蓋体２４との間に配置することができるのであれば、環状ではない部材を振動吸収部材６０Ａとして採用してもよい。例えば、複数の振動吸収部材６０Ａを、周方向に沿って配置するようにしてもよい。 -In 2nd Embodiment, if it can arrange | position between the flange 263 and the cover body 24 of the spring receiving member 26, you may employ | adopt the member which is not cyclic | annular as the vibration absorption member 60A. For example, a plurality of vibration absorbing members 60A may be arranged along the circumferential direction.
・各実施形態において、振動吸収部材６０，６０Ａを、圧力調整弁１０よりも下流で発生した圧力脈動に起因するばね受け部材の振動を抑えることができるのであれば、シリコーン以外の他の樹脂で構成した振動吸収部材を採用してもよい。 In each embodiment, the vibration absorbing members 60 and 60A may be made of a resin other than silicone as long as the vibration of the spring receiving member due to pressure pulsation generated downstream of the pressure regulating valve 10 can be suppressed. You may employ | adopt the comprised vibration absorption member.
・振動吸収部材は、ばね受け部材２６の振動を減衰させることができるのであれば、任意の構成であってもよい。例えば、グリースなどの液体を樹脂製の袋内に封入した構成のものを振動吸収部材として採用してもよい。 The vibration absorbing member may have any configuration as long as the vibration of the spring receiving member 26 can be attenuated. For example, a configuration in which a liquid such as grease is sealed in a resin bag may be adopted as the vibration absorbing member.
・各実施形態では、圧力調整弁を、流体の一例であるＣＮＧを内燃機関の吸気通路内に供給する経路に配置する圧力調整弁に具体化したが、ＣＮＧ以外の他の気体やオイルなどの液体を供給する経路に配置する圧力調整弁に具体化してもよい。 In each embodiment, the pressure adjustment valve is embodied as a pressure adjustment valve that is arranged in a path for supplying CNG, which is an example of a fluid, into the intake passage of the internal combustion engine. You may embody in the pressure regulation valve arrange | positioned in the path | route which supplies a liquid.
１０…圧力調整弁、２２…ハウジング、２４…ハウジングの底壁の一例を構成する蓋体、２４１…突出部、２４２…支持用孔、２５…支持部材の一例である調整スクリュ、２６…ばね受け部材、２６１…ばね受け本体、２６３…フランジ、２７…ピストン、２８…調圧用スプリング、６０，６０Ａ…振動吸収部材、６１…肉厚部、６２…肉薄部、Ｚ…軸方向。 DESCRIPTION OF SYMBOLS 10 ... Pressure adjustment valve, 22 ... Housing, 24 ... Cover body which constitutes an example of bottom wall of housing, 241 ... Projection, 242 ... Support hole, 25 ... Adjustment screw which is an example of support member, 26 ... Spring receiver 261 ... Spring receiving body, 263 ... Flange, 27 ... Piston, 28 ... Pressure adjusting spring, 60, 60A ... Vibration absorbing member, 61 ... Thick part, 62 ... Thin part, Z ... Axial direction.
Claims (7)
前記ピストンが進退移動する方向を軸方向とした場合、同ピストンの前記軸方向における位置に応じた量の流体を出力する圧力調整弁において、
前記支持部材よりも径方向外側であって、且つ前記底壁と前記ばね受け部材との間となる位置には、前記底壁及び前記ばね受け部材の双方に接触する振動吸収部材が設けられている
ことを特徴とする圧力調整弁。 A housing having a bottomed cylindrical shape, a piston disposed in the housing, moving in a direction approaching and away from the bottom wall of the housing, and a biasing force in a direction away from the bottom wall. A spring that is applied to the spring, a spring receiving member that supports the spring, and a support member that is supported by the bottom wall and supports the spring receiving member.
When the direction in which the piston moves forward and backward is the axial direction, in the pressure regulating valve that outputs an amount of fluid according to the position of the piston in the axial direction,
A vibration absorbing member that contacts both the bottom wall and the spring receiving member is provided at a position that is radially outside the support member and between the bottom wall and the spring receiving member. A pressure regulating valve characterized by
請求項１に記載の圧力調整弁。 The pressure regulating valve according to claim 1, wherein the vibration absorbing member has an annular shape.
前記支持部材は、その先端が前記支持用孔から前記ピストン側に突出する態様で前記底壁に支持されており、
前記ばね受け部材は、
前記支持部材の先端に接触するとともに、径方向外側の端部が前記突出部の先端よりも前記軸方向において前記底壁の近くに位置するばね受け本体と、
同ばね受け本体の前記径方向外側の端部に接続され、前記スプリングを支持する環状のフランジと、を有し、
前記振動吸収部材は、前記軸方向に延びる筒状部材であり、前記ハウジングの前記突出部の外周面と、前記ばね受け本体において同突出部の外周面に対向する面との双方に接触している
請求項１又は請求項２に記載の圧力調整弁。 The bottom wall of the housing has a protruding portion that protrudes toward the piston in the axial direction, and the bottom wall is provided with a support hole that penetrates in the axial direction and opens at the tip of the protruding portion. ,
The support member is supported by the bottom wall in such a manner that a tip thereof protrudes from the support hole to the piston side,
The spring receiving member is
A spring receiving body that is in contact with the tip of the support member and whose radially outer end is located closer to the bottom wall in the axial direction than the tip of the protrusion;
An annular flange connected to the radially outer end of the spring receiving body and supporting the spring;
The vibration absorbing member is a cylindrical member extending in the axial direction, and is in contact with both an outer peripheral surface of the projecting portion of the housing and a surface facing the outer peripheral surface of the projecting portion in the spring receiving body. The pressure regulating valve according to claim 1 or 2.
前記肉厚部は、前記ハウジングの前記突出部と前記ばね受け部材の前記ばね受け本体との双方に接触し、
前記肉薄部は、前記ハウジングの前記突出部及び前記ばね受け本体の何れか一方のみに接触している
請求項３に記載の圧力調整弁。 The vibration absorbing member has a configuration in which a thick portion having a wide width in the radial direction and a thin portion having a width in the radial direction narrower than the thick portion are aligned in the axial direction.
The thick portion is in contact with both the protruding portion of the housing and the spring receiving body of the spring receiving member,
The pressure regulating valve according to claim 3, wherein the thin portion is in contact with only one of the projecting portion of the housing and the spring receiving body.
請求項４に記載の圧力調整弁。 The pressure according to claim 4, wherein the vibration absorbing member includes at least two thick portions, and the thick portions and the thin portions are alternately arranged along the axial direction. tuning valve.
前記振動吸収部材は、円盤状をなすとともに、前記ハウジングの底壁と前記フランジとの間に配置されており、
前記振動吸収部材の外径は前記スプリングの外径以上であり、前記振動吸収部材の内径は前記スプリングの内径以下である
請求項２に記載の圧力調整弁。 The spring receiving member has a spring receiving body that contacts the tip of the support member, and an annular flange that is connected to the radially outer end of the spring receiving body and supports the spring,
The vibration absorbing member has a disk shape and is disposed between the bottom wall of the housing and the flange,
The pressure regulating valve according to claim 2, wherein an outer diameter of the vibration absorbing member is equal to or larger than an outer diameter of the spring, and an inner diameter of the vibration absorbing member is equal to or smaller than an inner diameter of the spring.
請求項１〜請求項６のうち何れか一項に記載の圧力調整弁。 The pressure regulating valve according to any one of claims 1 to 6, wherein the vibration absorbing member is made of resin.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015080130A JP2016200947A (en) | 2015-04-09 | 2015-04-09 | Pressure regulating valve |
| PCT/JP2016/061278 WO2016163406A1 (en) | 2015-04-09 | 2016-04-06 | Pressure regulation valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015080130A JP2016200947A (en) | 2015-04-09 | 2015-04-09 | Pressure regulating valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2016200947A true JP2016200947A (en) | 2016-12-01 |
Family
ID=57072330
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2015080130A Ceased JP2016200947A (en) | 2015-04-09 | 2015-04-09 | Pressure regulating valve |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2016200947A (en) |
| WO (1) | WO2016163406A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110776967B (en) * | 2019-11-13 | 2021-03-02 | 新奥(舟山)液化天然气有限公司 | Liquid natural gas separation and recovery device |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000276236A (en) * | 1999-03-24 | 2000-10-06 | Nippon Carbureter Co Ltd | Pressure regulator |
| JP2011108057A (en) * | 2009-11-19 | 2011-06-02 | Jtekt Corp | Pressure reducing valve |
| JP2015118411A (en) * | 2013-12-16 | 2015-06-25 | 株式会社不二工機 | Pressure reduction valve, and seal member between opening used therefor |
-
2015
- 2015-04-09 JP JP2015080130A patent/JP2016200947A/en not_active Ceased
-
2016
- 2016-04-06 WO PCT/JP2016/061278 patent/WO2016163406A1/en active Application Filing
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000276236A (en) * | 1999-03-24 | 2000-10-06 | Nippon Carbureter Co Ltd | Pressure regulator |
| JP2011108057A (en) * | 2009-11-19 | 2011-06-02 | Jtekt Corp | Pressure reducing valve |
| JP2015118411A (en) * | 2013-12-16 | 2015-06-25 | 株式会社不二工機 | Pressure reduction valve, and seal member between opening used therefor |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2016163406A1 (en) | 2016-10-13 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US9719575B2 (en) | Vibration-damping device | |
| JP6652895B2 (en) | Damping force adjustable shock absorber | |
| JPWO2010126060A1 (en) | Vibration isolator | |
| JP2012172832A (en) | Liquid-sealed type vibration control device | |
| US9566856B2 (en) | Fluid-filled vibration damping device | |
| JP2009103223A (en) | Vibration damper | |
| JP2016200947A (en) | Pressure regulating valve | |
| JP2012107763A (en) | Vibration isolating device | |
| JP4976056B2 (en) | Vibration isolator | |
| JP5116451B2 (en) | Hydraulic shock absorber | |
| WO2014002781A1 (en) | Vibration-damping device | |
| CN103363013A (en) | A fluid-enclosed vibration-isolating device | |
| JP2009299751A (en) | Shock absorber | |
| JP2016044776A (en) | Pressure buffer device | |
| JP2018115718A (en) | Vibration control device | |
| JP2021067295A (en) | Fluid-sealed type vibration isolation device | |
| JP5291537B2 (en) | Vibration isolator | |
| JP2016188649A (en) | Valve device | |
| JP2007120566A (en) | Vibration isolator | |
| JP5723944B2 (en) | Vibration isolator | |
| JP6207866B2 (en) | Liquid-filled vibration isolator | |
| JP6391162B2 (en) | Vibration isolator | |
| JP2007239552A (en) | Pressure pulsation damping device | |
| JP5275884B2 (en) | Liquid filled vibration isolator | |
| JP2009191999A (en) | Vibration absorbing device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A621 | Written request for application examination |
Free format text: JAPANESE INTERMEDIATE CODE: A621 Effective date: 20171114 |
|
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 Effective date: 20180710 |
|
| A045 | Written measure of dismissal of application [lapsed due to lack of payment] |
Free format text: JAPANESE INTERMEDIATE CODE: A045 Effective date: 20181127 |